Engine valve train device

ABSTRACT

In an engine valve train device in which a crankshaft sprocket  25   b  provided on a crankshaft  8  and an intermediate sprocket  38   a  disposed in the vicinity of camshafts  36, 37  are connected by means of a timing chain  40  and an intermediate gear  38   b  fixed to the intermediate sprocket  38   a  is made to mesh with camshaft gears  41, 42  fixed to the camshafts, the intermediate gear  38   b  is made smaller in diameter than the intermediate sprocket  38   a  and is disposed behind the intermediate sprocket  38 , and furthermore, an inspection hole  38   c ′ is formed in the intermediate sprocket  38   a  for visualizing the meshing portion between the intermediate gear  38   b  and the camshafts gears  41, 42.

TECHNICAL FIELD

The present invention relates to an engine valve train device in which a camshaft is driven to rotate by a crankshaft.

BACKGROUND ART

For example, as valve train devices for motorcycle engines, there exists conventionally a valve train device having a construction in which a crankshaft sprocket provided on a crankshaft and an intermediate sprocket disposed in the vicinity of a camshaft are connected by way of a timing chain, so that an intermediate gear fixed to the intermediate sprocket meshes with a camshaft gear fixed to the camshaft (for example, refer to JP-A-6-66111).

In the case of the construction in which the intermediate gear fixed to the intermediate sprocket is brought into mesh engagement with the camshaft gear, while a construction in which timing or alignment marks on the intermediate gear and the camshaft gear are caused to align with each other is adopted as a construction for carrying out valve timing, since the construction of the intermediate gear requires that the intermediate gear has a smaller diameter than that of the intermediate sprocket, in the event that the intermediate gear is disposed behind the intermediate sprocket, the alignment mark on the intermediate gear becomes difficult to be observed visually from the outside, and this causes a problem that the valve timing work becomes difficult to be carried out when an engine is assembled.

Note that in case a construction is adopted in which an intermediate gear is disposed in front of an intermediate sprocket (for example, refer to JP-A-9-250314), while the valve timing work becomes easy to be carried out, a dimension from the camshaft gear to the cam nose, and an area surrounding the camshaft is enlarged accordingly and the torsional amount of the camshaft becomes large, leading to a problem that the valve timing control accuracy is reduced.

The invention was made in view of the problems inherent in the conventional valve train device construction, and a problem that the invention is to solve is how to provide an engine valve train device which makes the valve timing work easy to be carried out while the intermediate gear is disposed behind the intermediate sprocket and which can improve the valve timing control accuracy while avoiding the risk that the area surrounding the camshaft is enlarged.

DISCLOSURE OF THE INVENTION

According to a first aspect of the invention, there is provided an engine valve train device in which an intermediate driven wheel disposed in the vicinity of a camshaft is driven by a crankshaft-side driving wheel formed on a crankshaft and a camshaft gear fixed to the camshaft is driven by an intermediate gear disposed on a support shaft on which the intermediate driven wheel is disposed, the intermediate gear integrally rotating with the intermediate driven wheel, the engine valve train device being characterized in that a reduction ratio from the crankshaft-side driving wheel to the intermediate driven wheel is set larger than a reduction ratio from the intermediate gear to the camshaft gear, in that the intermediate gear is made smaller in diameter than the intermediate driven wheel to such an extent that a pitch circle of the intermediate gear passes substantially an intermediate between a diameter of a boss and a pitch circle of the intermediate driven wheel and the intermediate gear is disposed on a back side of the intermediate driven wheel, in that an inspection hole is formed in the intermediate driven wheel for visualizing a meshing portion where the intermediate gear and the camshaft gear mesh with each other, and in that an alignment mark is formed on a tooth portion of the intermediate gear and the camshaft gear, respectively.

According to a second aspect of the invention, there is provided an engine valve train device as set forth in the first aspect of the invention, characterized in that the intermediate driven wheel and the intermediate gear are disposed on a crankshaft side across a mating surface of a cylinder head with a cylinder head cover, whereas the camshaft gear is disposed on an opposite side to the crankshaft side across the mating surface, and in that the meshing portion where the intermediate gear meshes with the camshaft gear is positioned in the vicinity of the mating surface.

According to a third aspect of the invention, there is provided an engine valve train device as set forth in the first or second aspect of the invention, characterized in that a position alignment mark which refers to the mating surface as a reference surface is formed on an outer surface of the intermediate driven wheel.

According to a fourth aspect of the invention, there is provided an engine valve train device as set forth in the second or third aspect of the invention, characterized in that a camshaft carrier is detachably attached to the cylinder head, and in that the camshaft is rotationally mounted on the camshaft carrier by means of a camshaft cap.

According to a fifth aspect of the invention, there is provided an engine valve train device as set forth in any of the first to fourth aspects of the invention, characterized in that the intermediate driven wheel is an intermediate sprocket around which a timing chain is wound and is formed integrally with the intermediate gear to constitute an intermediate rotational unit, and in that the intermediate rotational unit is disposed within a chain compartment formed on a side wall of the cylinder head in such a manner that a rotational shaft of the intermediate rotational unit is located closer to the crankshaft side than the mating surface and is rotationally supported via a bearing by a support shaft which is inserted to be disposed in such a manner as to extend across the chain compartment.

According to a sixth aspect of the invention, there is provided an engine valve train device as set forth in the fifth aspect of the invention, characterized in that a washer member is disposed between the intermediate rotational unit and a wall surface of the chain compartment for regulating an axial position of the intermediate rotational unit and an axial arrangement space for the bearing.

According to a seventh aspect of the invention, there is provided an engine valve train device as set forth in any of the first to sixth aspects of the invention, characterized in that the camshaft gear comprises a power transmission gear for transmitting a driving force from the intermediate gear to the camshaft and an adjustment gear for adjusting a backlash between the power transmission gear and the intermediate gear, the adjustment gear being made to rotate relative to the power transmission gear, whereby the backlash is adjusted by causing the adjustment gear to relatively rotate forward in a rotating direction relative to the power transmission gear.

According to an eighth aspect of the invention, there is provided an engine valve train device as set forth in the first aspect of the invention, characterized in that an alignment mark is formed on each tooth portion of an intake camshaft gear and an exhaust camshaft gear disposed on the intake camshaft and the exhaust camshaft respectively and on a tooth portion of the intermediate gear, in that the intermediate driven wheel is formed with an inspection hole for visualizing the alignment marks of the intake camshaft gear and the intermediate gear and an inspection hole for visualizing the alignment marks of the exhaust camshaft gear and the intermediate gear, and in that the alignment marks of the intake camshaft gear and the intermediate gear and the alignment marks of the exhaust camshaft gear and the intermediate gear are visible at the same time.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a right-hand side view of an engine according to an embodiment of the invention.

FIG. 2 is a sectional plan view showing a development of the engine.

FIG. 3 is a left-hand side view showing a valve train device of the engine.

FIG. 4 is a sectional rear elevation of the valve train device.

FIG. 5 is a sectional plan view showing a development of a balance shaft of the engine.

FIG. 6 is a bottom view of a cylinder head of the engine.

FIG. 7 is a bottom view of a cylinder body of the engine.

FIG. 8 is a sectional side view showing a portion where the cylinder head of the engine is connected to the cylinder body.

FIG. 9 is a sectional side view showing a portion where the cylinder body of the engine is connected to the crankcase.

FIG. 10 is another sectional side view showing a portion where the cylinder body of the engine is connected to the crankcase.

FIG. 11 is a left-hand side view showing a balancer unit of the engine.

FIG. 12 is an enlarged cross-sectional view of a portion where a holding lever of the balancer unit is attached.

FIG. 13 is a side view of constituent components of a rotational lever of the balancer unit.

FIG. 14 is a side view showing a damping construction of a balancer drive gear of the balancer unit.

FIG. 15 is a right-hand side view of the balancer unit.

FIG. 16 is a sectional right-hand side view of a bearing bracket of the engine.

FIG. 17 is a sectional left-hand side view of a bearing bracket.

FIG. 18 is an explanatory drawing showing the construction of a lubrication system of the engine.

FIG. 19 is a drawing showing the construction of the lubrication system.

FIG. 20 is a sectional side view of an area surrounding a lubricating oil pump of the lubrication system.

FIG. 21 is a sectional left-hand side view of the lubrication system.

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, an embodiment of the invention will be described with reference to the accompanying drawings.

FIGS. 1 to 21 are drawings for describing an embodiment of the invention. In the drawings, reference numeral 1 denotes a water-cooled, 4-cycle, single cylinder, 5-valve engine, and in general, the engine has a construction in which a cylinder body 3, a cylinder head 4 and a cylinder head cover 5 are stacked on and fastened to a crankcase 2, and a piston 6 slidably disposed in a cylinder bore 3 a in the cylinder body 3 is connected to a crankshaft 8 via a connecting rod 7.

The cylinder body 3 and the crankcase 2 are securely connected together by screwing four case bolts 30 a which pass through a lower flange portion (a case side flange portion) 3 b into a cylinder side mating surface 2 e of the crankcase 2. To be more specific, the case bolts 30 a are screwed into bolt connecting portions (connecting boss portions) 12 c of iron alloy bearing brackets (bearing members) 12, 12′ (which will be described later on) embedded in left and right wall portions of the aluminum alloy crankcase 2, respectively, through insert casting. Note that reference numeral 31 a denotes a positioning dowel pin for positioning the crankcase 2 and the cylinder body 3.

In addition, the cylinder body 3 and the cylinder head 4 are connected together with two short head bolts 30 b and four long head bolts 30 c. The short head bolt 30 b is screwed to be planted in a portion below an induction port 4 c and a portion below an exhaust port in the cylinder head 4, extends downwardly to pass through an upper flange portion 3 f of the cylinder block 3 and protrudes downwardly therefrom. Then, a cap nut 32 a is screwed on the downwardly protruding portion of the short head bolt 30 b, whereby the upper flange portion 3 f and hence the cylinder body 3 are fastened to a cylinder side mating surface 4 a of the cylinder head 4.

In addition, the long head bolt 30 c is screwed to be planted in the lower flange portion 3 b of the cylinder body 3, extends upwardly to pass from the upper flange portion 3 f of the cylinder block 3 through a flange portion 4 b of the cylinder head 4 and protrudes upwardly therefrom. Then, a cap nut 32 b is screwed on the upwardly protruding portion of the long head bolt 30 c, whereby the lower flange portion 3 b and hence the cylinder body are fastened to the cylinder side mating surface 4 a of the cylinder head 4.

Thus, in connecting the cylinder body 3 and the cylinder head 4 together, since not only the upper flange portion 3 f of the cylinder body 3 is fastened to be fixed to the cylinder head 4 with the short head bolts 30 b and the cap nuts 32 but also the long head bolts 30 c are planted in the lower flange portion 3 b which is fastened to be securely connected to the mating surface 2 e of the crankcase 2, so that the cylinder body 3 is fastened to be fixed to the flange portion 4 b of the cylinder head 4 with the long head bolts 30 c and the cap nuts 32 b, a tensile load generated by a combustion pressure comes to be borne by the cylinder body 3 and the four long head bolts 30 c, so that a load applied to the cylinder body 3 can be reduced accordingly or by such an extent that the load is so borne by the cylinder body 3 and the long head bolts 30 c. As a result, a stress generated at, in particular, an axially intermediate portion of the cylinder body 3 can be reduced, thereby making it possible to secure a required durability even in case the thickness of the cylinder body 3 is reduced.

Incidentally, in the event that only the upper flange portion 3 f of the cylinder body 3 is connected to the cylinder head 4, an excessively large tensile stress is generated at the axially intermediate portion of the cylinder body 3, and in an extreme case, there occurs a concern that a crack is generated at the portion in question. In the embodiment, however, the generation of the excessively large stress at the intermediate portion of the cylinder body can be avoided due to the presence of the long head bolts 30 c, thereby making it possible to prevent the generation of a crack.

In addition, in planting the long head bolts 30 c in the lower flange portion 3 b, since the long head bolts are disposed in the vicinity of the crankcase fastening case bolts 30 a, respectively, the load generated by the combustion pressure can be transmitted from the cylinder head 4 to the crankcase 2 via the long head bolts 30 c and the cylinder body in an ensured fashion, thereby making it possible to improve the durability against the load in this respect.

Here, as shown in FIGS. 5, 16, the right-side bearing bracket 12′ has a boss portion 12 b in which a right-side bearing 11 a′ of the crankshaft 8 is inserted to be fitted in a bearing hole 12 a through press fit. Then, the bolt connecting portions 12 c, 12 c extend upwardly from front and rear portions which hold the crankshaft 8 therebetween as seen in the direction in which the crankshaft 8 extends to the vicinity of the cylinder-side mating surface 2 e of the crankcase 2.

In addition, in the left-side bearing bracket 12, as shown in FIGS. 5, 17, the bolt connecting portions 12 c, 12 c extend from front and rear portions which hold the crankshaft 8 therebetween as seen in the direction in which the crankshaft 8 extends to the vicinity of the cylinder-side mating surface 2 e of the crankcase 2. In addition, a collar hole 12 e is formed in the boss portion 12 b into which an iron bearing collar 12 d having an outside diameter larger than that of a balancer driving gear 25 a, which will be described later on, is press fitted. Then, a left-side crankshaft bearing 11 a is inserted to be fitted in the bearing hole 12 a of the bearing collar 12 d.

Here, the bearing collar 12 d is such as to facilitate the assembly of the crankshaft 8 in the crankcase 2 with a gear unit 25 having the balancer driving gear 25 a being press fitted on the crankshaft 8.

In addition, as shown in FIG. 5, a seal plate 25 d is interposed between the gear unit 25 on a left shaft portion 8 c of the crankshaft 8 and the bearing 11 a. An inside diameter side portion of the seal plate 25 d is held by the gear unit 25 and an inner race of the bearing 11 a, and a slight gap is provided between an outside diameter side portion thereof and an outer race of the bearing 11 a for avoiding the interference therebetween. In addition, an inner circumferential surface of a flange portion 12 h of the bearing collar 12 d is brought into sliding contact with an outer circumferential surface of the seal plate 25 d.

Furthermore, a seal tube 17 i is interposed between the bearing 11 a′ of a right shaft portion 8 c′ of the crankshaft 8 and a cover plate 17 g. An inner circumferential surface of the seal tube 17 i is fixedly fitted on the right shaft portion 8 c′. In addition, a seal groove having a labyrinth construction is formed in an outer circumferential surface of the seal tube 17 i, and the outer circumferential surface of the seal tube 17 i is brought into sliding contact with an inner circumferential surface of a seal bore 2 p formed in the right case portion 2 b.

Thus, the leakage of pressure within a crank compartment 2 c is prevented by interposing the seal plate 25 d and the seal tube 17 i on the outside of the bearings 11 a, 11 a′ on the left and right shaft portions 8 c, 8 c′ of the crankshaft 8.

Thus, according to the embodiment, since the bolt connecting portions (the connecting boss portions) 12 c, 12 c which extend toward the cylinder body 3 side are integrally formed on the sides situated opposite across the cylinder bore axis A of each of the iron alloy crankshaft supporting bearing members 12, 12′ which are insert cast in the aluminum alloy crankcase 2 and the case bolts 30 a for connecting the cylinder body 3 to the crankcase 2 are screwed into the bolt connecting portions 12 c, respectively, the load generated by virtue of the combustion pressure can be borne uniformly by the two front and rear bolt connecting portions 12 c which are situated opposite across the cylinder bore axis A, whereby the connecting rigidity between the cylinder body 3 and the crankcase 2 can be improved.

In addition, since balance shafts 22, 22′ which are disposed in parallel with the crankshaft 8 in the vicinity thereof are supported by the iron alloy bearing members 12, 12′ at at least one ends thereof, the supporting rigidity of the balance shafts 22, 22′ can be increased.

Furthermore, in embedding the iron alloy bearing brackets 12, 12′ in the aluminum alloy crankcase 2, since the upper end face 12 f of the bolt connecting portion 12 c is positioned inwardly without being exposed to the cylinder side mating surface 2 e of the crankcase 2, there is no risk that metallic members which are different in hardness and material exist in a mixed fashion at a joint between the crankcase 2 and the cylinder block 3, thereby making it possible to avoid a reduction in sealing capability. Namely, in the event that the upper end face 12 f of the bolt connecting portion 12 c abuts with a case side mating surface formed on the lower flange 3 b of the aluminum alloy cylinder body 3, the sealing capability is reduced due to a difference in thermal expansion coefficients.

In addition, in the left-side bearing bracket 12, since the bearing collar 12 having the outside diameter larger than that of the balancer driving gear 25 a is attached to the outer circumference of the bearing 11 a, when assembling the crankshaft 8 in the crankcase 2 with the balancer driving gear 25 a being attached to be fixed onto the crankshaft 8 through press fit or the like (or the balance driving gear 25 a may of course be integrally formed on the crankshaft 8), there is caused no risk that the balancer driving gear 25 a is brought into interference with a minimum inside diameter portion of the boss portion 12 b of the bearing bracket 12, and hence the assembling of the crankshaft 8 can be implemented without any problem.

The crankcase 2 is a two-piece type in which the crankcase 2 is divided into the left and right case portions 2 a, 2 b. A left case cover 9 is detachably attached to the left case portion 2 a, and a space surrounded by the left case portion 2 a and the left case cover 9 constitutes a flywheel magnet compartment 9 a. A flywheel magnetic generator 35 attached to the left end portion of the crankshaft 8 is accommodated in this flywheel magnet compartment 9 a. Note that the flywheel magnet compartment 9 a communicates with a camshaft arranging compartment via chain compartments 3 d, 4 d, which will be described later on, whereby most of the lubricating oil which has been used to lubricate camshafts falls into the flywheel magnet compartment 9 a via the chain compartments 3 d, 4 d.

In addition, a right case cover 10 is detachably attached to the right case portion 2 b, and a space surrounded by the right case portion 2 b and the right case cover 10 constitutes a clutch compartment 10 a.

The crank compartment 2 c and a transmission compartment 2 d are formed at front and rear portions of the crankcase 2, respectively. The crank compartment 2 c is made to open to the cylinder bore 3 a but is defined substantially to be separated from the other compartments such as the transmission compartment 2 d. Due to this, the pressure within the transmission compartment 2 d is caused to fluctuate as the piston reciprocates vertically, thereby allowing the transmission compartment 2 d to function as a pump.

The crankshaft 8 is arranged such that left and right arm portions 8 a, 8 a and left and right weight portions thereof are accommodated in the crank compartment 2 c. The crankshaft 8 is an assembly including a left crankshaft portion into which the left arm portion 8 a, weight portion 8 b and shaft portion 8 c are integrated and a right crankshaft portion into which the right arm portion 8 a, weight portion 8 b and shaft portion 8 c′ are integrated, the left crankshaft portion and the right crankshaft portion being connected integrally via a tubular crank pin 8 d.

The left and right shaft portions 8 c, 8 c′ are rotationally supported on the side walls of the left and right case portions 2 a, 2 b via the crankshaft bearings 11 a, 11 a′. As has been described above, the bearings 11 a, 11 a′ are press fitted in the bearing holes 12 a in the iron alloy bearing brackets 12, 12′ which are insert cast in the left and right case portions 2 a, 2 b of aluminum alloy.

A transmission 13 is accommodated and arranged in the transmission compartment 2 d. The transmission 13 is such as to have a constant mesh construction in which a main shaft 14 and a drive shaft 15 are provided and arranged in parallel with the crankshaft 8, and first-speed to fifth-speed gears 1 p to 5 p attached to the main shaft 14 are made to constantly mesh with first-speed to fifth-speed gears 1 w to 5 w attached to the drive shaft 15.

The main shaft 14 is rotationally supported by the left and right case portions 2 a, 2 b via main shaft bearings 11 b, 11 b, whereas the drive shaft 15 is rotationally supported by the left and right case portions 2 a, 2 b via drive shaft bearings 11 c, 11 c.

A right end portion of the main shaft 14 passes through the right case portion 2 b and protrudes to the right side, and a clutch mechanism 16 is attached to the protruding portion, and this clutch mechanism 16 is located within the clutch compartment 10 a. Then, a large reduction gear (an input gear) 16 a of the clutch mechanism 16 meshes with a small reduction gear 17 fixedly attached to the right end portion of the crankshaft 8.

A left end portion of the drive shaft 15 protrudes outwardly from the left case portion 2 a and a driving sprocket 18 is attached to the protruding portion. This driving sprocket 18 is connected to a driven sprocket on a rear wheel.

A balancer unit 19 according to the embodiment includes front and rear balancers 20, 20′ disposed opposite across the crankshaft 8 and having substantially the same construction. The front and rear balancers 20, 20′ include the balance shaft 22, 22′ which do not rotate and weights 24, 24 which are rotationally supported on the balance shat via bearings 23, 23.

Here, the balance shafts 22, 22′ are also used as the case bolts (the connecting bolts) for connecting the left and right case portions 2 a, 2 b together in the direction in which the crankshaft extends. The respective balance shafts 22, 22′ function to connect the left and right case portions together by causing flange portions 22 a formed on insides of the rotationally supported weights 24 in a transverse direction of the engine to abut with boss portions 12 g of the bearing brackets 12′, 12 which are insert cast into the left and right case portions 2 a, 2 b and screwing fixing nuts 21 a, 21 b on opposite ends of the respective balance shafts.

The weight 24 includes a semi-circular weight main body 24 a and a circular gear supporting portion 24 b which is integrally formed on the weight main body, and a ring-shaped balancer driven gear 24 c is fixedly attached to the gear supporting portion 24 b. Note that reference numeral 24 b denotes a hole made by partially cutting away the material of a part of the weight 24 which is situated opposite to the weight main body 24 a so as to reduce the weight of the part to as low a level as possible.

The balancer driven gear 24 c attached to the rear balancer 20′ meshes with the balancer driving gear 25 a which is rotationally attached relative to the gear unit 25 which is securely attached to the left shaft portion 8 c of the crankcase 8 through press fit.

Note that reference numeral 25 b denotes a timing chain driving sprocket integrally formed on the gear unit 15 and has, as shown in FIG. 11, an aligning or timing mark 25 c for alignment of timing marks for valve timing. The gear unit 25 is press fitted on the crankshaft 8 such that the timing mark 25 c aligns with the cylinder bore axis A as viewed in the direction in which the crankshaft extends when the crankshaft 8 is situated at a top dead center of a compression stroke.

In addition, the balancer driven gear 24 c attached to the front balancer 20 meshes with a balancer driving gear 17 a which is supported rotationally relative to the small reduction gear 17 which is fixedly attached to the right shaft portion 8 c′ of the crankshaft 8.

Here, the rear balancer driving gear 25 a is supported rotationally relative to the gear unit 25, and the front balancer driving gear 17 a is supported rotationally relative to the small reduction gear 17. Then, U-shaped damper springs 33 each made up of a plate spring are interposed between the balancer driving gears 25 a, 17 a and the gear unit 25 and the small reduction gear 17, respectively, to thereby restrain the transmission of impact generated due to a torque fluctuation occurring in the engine to the balancers 20, 20′ is restrained from being transmitted.

Here, while the balancer driving gear 17 a for driving the front balancer 20 will be described in detail by reference to FIG. 14, the same description would be given if the balancer driving gear 25 a for driving the rear balancer were described. The balancer driving gear 17 a is formed into a ring shape and is supported by a sliding surface 17 b formed so as to have a smaller diameter than the small reduction gear 17 rotationally relative to a side of the small reduction gear 17. Then, a number of U-shaped spring retaining grooves 17 c are formed in the sliding surface 17 b by setting them back into the surface thereof in a radial fashion about the center of the crankshaft, and the U-shaped damper springs 33 are arranged to be inserted in place within the spring retaining grooves 17 c. Opening side end portions 33 a, 33 a of the damper spring 33 are locked at front and rear stepped portions formed in a locking recessed portion 17 d formed in an inner circumferential surface of the balancer driving gear 17 a.

When a relative rotation is generated between the small reduction gear 17 and the balancer driving gear 17 a due to a torque fluctuation, the damper springs 33 resiliently deform in a direction in which the space between the end portions 33 a, 33 a narrows so as to absorb the torque fluctuation so generated. Note that reference numeral 17 g denotes a cover plate for retaining the damper springs 33 within the retaining grooves 17 c, reference numeral 17 h denotes a key for connecting the small reduction gear 1 with the crankshaft 8, and reference numerals 17 e, 17 f denote, respectively, alignment marks for use in assembling the small reduction gear 17 and the balancer driving gear 17 a.

A mechanism for adjusting a backlash between the balancer driven gears 24 c, 24 c and the balancer driving gears 25 a, 17 a is provided on the balancers 20, 20′. This adjusting mechanism is constructed such that the balancer axis of the balance shaft 22, 22′ slightly deviates from the rotational center of the balancer driven gear 24 c. Namely, when the balance shaft 22, 22′ is made to rotate about the balancer axis, the space between the rotational center line of the balancer driven gear 24 c and the rotational center line of the balancer driving gear 25 a, 17 a changes slightly, whereby the backlash is changed.

Here, a mechanism for rotating the balance shaft 22, 22′ differs between the front balancer 20 and the rear balancer 20′. Firstly, in the rear balancer 20′, a hexagonal locking protruding portion 22 b is formed on a left end portion of the rear balance shaft 22′, and a spline-like (a polygonal star-like) locking hole 26 a formed in one end of a rotational lever 26 is locked on the locking protruding portion 22 b. In addition, an arc-like bolt hole 26 b is formed in the other end portion of the rotational lever 26 in such a manner as to extend about the balancer axis.

A fixing bolt 27 a passed through the bolt hole 26 b is planted in a guide plate 28. The guide plate 28 is generally formed into an arc-like shape and is fixedly bolted to the crankcase 2. Note that the guide plate 28 has also a function to control the flow of lubricating oil.

The adjustment of the backlash of the rear balancer 20′ is implemented by rotating the rotational lever 26 so as to bring the backlash to an appropriate state with the fixing nut 21 a being loosened and there after by fixing the rotational lever 26 with the fixing bolt 27 a and a fixing nut 27 b, and thereafter, the fixing nut 21 a is refastened.

A grip portion 22 f having an oval cross section, which is formed by forming a flat portion 22 e on both sides of a cross-sectionally circular shape, is formed on a left end portion of the front balance shaft 22 (refer to FIG. 12). A collar 29 a having an inner circumferential shape which matches an outer circumferential shape of the grip portion 22 f is attached to the grip portion 22 f, and furthermore, a holding portion 29 b of a holding lever 29 is attached to an outside of the collar 29 a in such a manner as to move axially but as not to rotate relatively. A distal end portion 29 e of the holding lever 29 is fixed to a boss portion 2 f of the left case portion 2 a with a bolt 29 f. In addition, a tightening slit 29 c is formed in the holding portion 29 b of the holding lever 29, so that the rotation of the collar 29 and hence of the balance shaft 22 is prevented by tightening up the fixing bolt 29 d. Furthermore, the fixing nut 21 b is screwed on the balance shaft 22 to an outer side of the collar 29 so as to be secured thereto via washer.

The adjustment of the backlash of the front balancer 20 is implemented by loosening the fixing nut 21 b or preferably removing the same, griping the grip portion 22 f of the balance shaft 22 with a tool to rotate the shaft so as to bring the backlash to an appropriate state, and thereafter tightening up the fixing bolt 29 d, and thereafter, the fixing nut 21 b is fastened.

In addition, a lubricating oil introducing portion 22 c is formed in an upper portion of the locking protruding portion 22 b by cutting out the upper in an arc. A guide bore 22 d is made to open to the introducing portion 22 c, and the guide bore extends into the balance shaft 22 and passes therethrough to below an outer circumferential surface of the balance shaft 22, whereby the lubricating oil introducing portion 22 c is made to communicate with an inner circumferential surface of the balancer bearing 23. Thus, lubricating oil that has fallen in the lubricating oil introducing portion 22 c is supplied to the balancer bearing 23.

Here, while the weight 24 and the balancer driven gear 24 c are disposed at the right end portion along the direction in which the crankshaft extends in the front balancer 20, in the rear balancer 20′, they are disposed at the left end portion. In addition, the balancer driven gear 24 c is located rightward relative to the weight 24 in both the front and rear balancers 20, 20′, and therefore, the weight 24 and the balancer driven gear 24 c are set into the same configuration in both the front and rear balancers.

Thus, according to the embodiment, since the weight main body 24 a and the balancer driven gear 24 c of the balancer 20 are disposed on the right-hand side (one side) of the front balance shaft (the primary balance shaft) 22 along the direction in which the crankshaft extends and the weight main body 24 a and the balancer driven gear 24 c are disposed on the left-hand side (the other side) of the rear balance shaft (the secondary balance shaft) 22′ along the direction in which the crankshaft extends, the reduction in balance in weight in the crankshaft direction that would result when providing a two-shaft balancer unit can be avoided.

In addition, since the front and rear balance shafts 22, 22′ are made to double as the case bolts for connecting the left and right case portions 2 a, 2 b together, when adopting a two-shaft balancer unit, the connecting rigidity of the crankcase can be enhanced while restraining the construction of the engine from becoming complex and the number of components from being increased.

Additionally, since the balancer weight main body 24 a and the balancer driven gear 24 c are made integral and are supported rotationally by the balance shafts 22, 22′, respectively, only the weight made up of the balancer weight main body 24 a and the balancer driven gear 24 c may be driven to rotate, and therefore, the engine output can be attempted to be used effectively to such an extent that the balance shafts themselves do not need to be driven to rotate.

In addition, the degree of freedom in assembling can be improved when compared with an engine construction in which a balancer weight and a balance shaft are made integral.

Additionally, since the rotational center lines of the balancer driven gears 24 c are caused to deviate relative to the axes of the balance shafts 22, 22′, the backlash between the balancer driven gears 24 c and the balancer driving gears 25 a, 27 a on the crankshaft 8 side can be adjusted by the simple construction or only by a simple operation of rotating the balance shafts, thereby making it possible to prevent the generation of noise.

On the front balance shaft 22, the backlash adjustment is implemented by gripping the grip portion 22 f formed on the left-hand side of the balance shaft 22 with a tool so as to rotate the balance shaft 22, and on the rear balance shaft 22′, the backlash adjustment is implemented by rotating the rotational lever 26 provided on the left-hand side of the balance shaft 22′. Thus, on either of the front and rear balance shafts 22, 22′, the backlash can be adjusted from the left-hand side of the engine, and hence the backlash adjusting work can be implemented efficiently.

Additionally, since the balancer driving gear 17 a on the crankshaft 8 side which meshes with the balancer driven gear 24 c is constructed to be disposed in such a manner as to rotate relatively to the sliding surface 17 b of the small reduction gear 17 which is fixed to the crankshaft 8 and the U-shaped damper springs 33 are disposed in the spring retaining grooves 17 c formed by setting them back from the sliding surface 17 b, the impact generated due to the torque fluctuation in the engine can be absorbed by the compact construction so that the balancer unit can be operated smoothly. Note that the same description can be made with respect to the balancer drive gear 25 a.

Furthermore, a coolant pump 48 is disposed at the right end portion of the front balance shaft 22 coaxially therewith. A rotating shaft of the coolant pump 48 is connected to the balance shaft 22 by an Oldham's coupling which has a similar construction to that of a lubricating oil pump 52, which will be described later on, in such a manner that a slight deviation between the centers of the rotating shaft and the balance shaft 22 can be absorbed.

In the valve train device of the embodiment, an intake camshaft 36 and an exhaust camshaft 37 which are disposed within the cylinder head cover 5 are constructed to be driven to rotate by the crankshaft 8. To be specific, a crankshaft sprocket a crankshaft side driving wheel) 25 b of the gear unit 25 press fitted on the left shaft portion 8 c of the crankshaft 8 so as to be attached thereto and an intermediate sprocket (an intermediate driven wheel) 38 a rotationally supported by a support shaft 39 planted in the cylinder head 4 are connected by a timing chain 40, and an intermediate gear 38 formed integrally on the intermediate sprocket 38 a and having a smaller diameter than that of the intermediate sprocket 38 a meshes with intake and exhaust gears 41, 42 secured to end portions of the intake and the exhaust camshafts 36, 37. Note that the timing chain 40 is disposed so as to pass through the chain compartments 3 d, 4 d formed on the left walls of the cylinder block 3 and the cylinder head 4.

The intermediate sprocket 38 a and the intermediate gear 38 b are formed so as to be integrated into an intermediate rotational unit 38 and are rotationally supported by the support shaft 39 which passes through the chain compartment 4 d on the cylinder head 4 in the direction in which the crankshaft extend along the cylinder bore axis A via two sets of needle bearings 44. The support shaft 39 is inserted from the outside of the cylinder head and is fixed at a flange portion 39 a thereof to the cylinder head 4 with two bolts 39 b. Note that reference numerals 39 c, 39 d denote a sealing gasket, respectively.

Here, commercially available (standard) bearings are adopted for the two sets of needle bearings 44, 44. A space adjusting collar 44 a is disposed between the respective bearings 44, 44, and thrust washers (washer members) 44 b, 44 b for receiving thrust load to thereby restrict the axial position of the intermediate rotational unit 38 are provided at ends of the bearings. The thrust washer 44 b is formed into a stepped shape having a large diameter portion which is brought into sliding contact with outer end faces of the intermediate sprocket and intermediate gear and a stepped portion 44 c which protrudes axially toward the needle bearing 44. The space where the bearing 44 is arranged is regulated by the stepped portion 44 c and the collar 44 a.

Thus, since the space adjusting collar 44 a is interposed between the two sets of bearings 44, 44, commercially available standard bearings can be adopted for the needle bearings by adjusting the length of the collar 44 a and the protruding amount of the stepped portion 44 c, thereby making it possible to reduce costs. Note that in the event that only one needle bearing is used, the space where the bearing is arranged is adjusted by the protruding amount of the stepped portion 44 c of the washer member.

In addition, since the washer having the stepped configuration is adopted as the thrust washer 44 b, the assembling work of the intermediate sprocket 38 a and the intermediate gear 38 b (the intermediate rotational unit) can be improved. Namely, in assembling the intermediate rotational unit to the engine, while the support shaft 39 is inserted from the outside in a state in which the intermediate sprocket 38 a and the intermediate gear 38 b are disposed within the chain compartment 4 d with the thrust washers being positioned at the ends of the intermediate sprocket 38 a and the intermediate gear 38 b in such a manner as not to fall therefrom, the thrust washer 44 b can be prevented from falling by allowing the stepped portion 44 c of the thrust washer 44 b to be locked in a shaft hole in the intermediate sprocket 38 a or the like, and hence the assembling properties can be improved.

In addition, an oil hole 39 e is formed in the support shaft 39 for supplying lubricating oil introduced from the cam compartment via an oil introducing bore 4 e formed in the cylinder head 4 to the needle bearing 44.

Additionally, four material cut-away weight reduction holes 38 c and two inspection holes 38 c adapted to be used at the time of assembling and made to double as material cut-away weight reduction holes are formed at intervals of 60 degrees. Then, an alignment or timing mark 38 d is stamped on a tooth situated substantially at the center of the inspection hole 38 c′ for the intermediate gear 38 b, and timing marks 41 a, 42 a are also stamped on two teeth of intake and exhaust camshaft gears 41, 42 which correspond to the timing marks 38 d. Here, when aligning the left and right timing marks 38 d, 38 d with the timing marks 41 a, 42 a, the intake and exhaust camshafts gears 41, 42 are located at positions, respectively, which correspond to a top dead center of a compression stroke.

Furthermore, timing marks 38 e, 38 e are also formed at portions of the intermediate sprocket 38 a which are situated on a cover side mating surface 4 f of the cylinder head 4 when the timing marks 38 d align with 41 a, 42 a.

Here, the intermediate rotational unit 38 is disposed on a crankshaft side of the cylinder head 4 which is beyond the cover side mating surface 4 f thereof, and the intake and exhaust camshafts 36, 37 are disposed on an opposite side to the crankshaft side. Then, a portion where the camshaft gears and the intermediate gear mesh with each other is positioned at substantially the same height of the mating surface 4 f, and therefore, the outer wall of the chain compartment 4 d does not constitute an interruption when the meshing portion is subjected to visual inspection through the inspection holes 38′.

Here, the intake and exhaust camshafts 36, 37 are rotationally supported by a camshaft carrier 80 in such a manner that the axes thereof are located at positions which are spaced away upwardly from the mating surface 4 f of the cylinder head 4. To describe in detail, the intake and exhaust camshafts 36, 37 are mounted on a bearing portion of a carrier main body 80 a detachably attached onto the mating surface 4 f and are held by a camshaft cap 80 b on an upper side thereof.

Note that, in FIG. 4, since a state in which the intake camshaft 36 is arranged is shown in an exploded fashion, while a bottom surface of the carrier main body 80 a is illustrated as being spaced away from the mating surface 4 a, in reality, the bottom surface of the carrier main body 80 a coincides with the mating surface 4 f, and this arrangement state is shown in FIG. 3.

To align valve timings, with the left case cover 9, the generator 35 and the cylinder head cover 5 being removed, firstly, the crankshaft 8 is held at a top dead center of a compression stroke by aligning the timing mark 25 c (refer to FIG. 11) with the cylinder bore axis A. In addition, the intermediate sprocket 38 a and the intermediate gear 38 b which are attached to the cylinder head 4 via the support shaft 39 are positioned so that the timing mark 38 e of the intermediate sprocket 38 a aligns with the cover side mating surface 4 f, and in this state, the crankshaft sprocket 25 b and the intermediate sprocket 38 a are connected by the timing chain 40. Then, the intake and exhaust camshaft gears 41, 42 on the intake and exhaust camshafts 36, 37 are brought into mesh engagement with the intermediate gear 38 b while confirming through the inspection hole 38 c′ that the timing marks 41 a, 42 a align with the timing mark 38 d on the intermediate gear 38 b, and the intake and exhaust camshafts 36, 37 are fixed to an upper surface of the cylinder head 4 via the camshaft carrier 80.

Thus, since the inspection holes 38 c′ made to double as the weight reduction holes to reduce the weight of the large diameter intermediate sprocket 38 a are provided in the intermediate sprocket 38 a, so that the alignment of the timing marks 38 d on the small diameter intermediate gear 38 b which is set on the back of the intermediate sprocket 38 a with the timing marks 41 a, 42 a on the camshaft gears 41, 42 can be confirmed through the inspection holes 38 c′, the meshing positions of the intermediate gear 38 b with the camshaft gears 41, 42 can visually confirmed in an easy and ensured fashion while the small diameter intermediate gear 38 b is placed on the back of the large diameter intermediate sprocket 38 a, thereby making it possible to align the valve timings without any problem.

In addition, since the intermediate gear 38 b can be disposed on the back side of the intermediate sprocket 38 a, the dimension from the camshaft gears 41, 42 which mesh with the intermediate gear 38 b to a cam nose 36 a can be made shorter, whereby the torsional angle of the camshaft can be made smaller to such an extent that the dimension is made so shorter, thereby making it possible to make compact an area surrounding the camshafts.

Namely, for example, in a case where the intermediate gear 38 b is disposed on a front side of the intermediate sprocket 38 a, while the valve timings can easily be aligned, the dimension from the camshaft gears 41, 42 to the cam nose becomes long, and the torsional angle of the camshafts becomes large to such an extent that the dimension is extended, thereby reducing the control accuracy of valve opening and closing timings.

In addition, in a case where the intermediate gear 38 b is disposed in front of the intermediate sprocket 38 a, a space between the intermediate sprocket support shaft 39 and the camshafts 36, 37 needs to be expanded in order to avoid any interference between the intermediate sprocket 38 a and the camshaft 36, 37, this causing a concern that the area surrounding the camshafts is enlarged.

Additionally, since the intermediate rotational unit 38 is arranged on the crankshaft side of the cylinder head 4 across the mating surface 4 f of the cylinder head 4 with the cylinder head cover 5 and the camshaft gears 41, 42 are arranged on the opposite side to the crankshaft side, the meshing portion where the camshaft gears 41, 42 mesh with the intermediate gear 38 b can be positioned in the vicinity of the mating surface 4 f, and the meshing portion can easily be visually inspected from the outside.

Namely, since the camshafts 36, 37 are disposed upwardly away from the mating surface 4 f, while the intermediate sprocket 38 a and the intermediate gear 38 b are positioned within the chain compartment 4 d, the meshing portion is positioned in the vicinity of the mating surface 4 f, and therefore, there is caused no risk that the outer wall of the chain compartment 4 d constitutes an interruption when the meshing portion is visually inspected through the inspection holes 38 c′.

In addition, since the position alignment mark 38 e which refers to the mating surface 4 f as a reference surface is formed on the outer surface of the intermediate sprocket 38 a, the angular positioning of the intermediate sprocket 38 a which is needed in the first place when adjusting the valve timing can be implemented easily and securely.

Additionally, since the camshaft carrier 80 is detachably attached to the cylinder head 4 and the camshafts 36, 37 are rotationally supported by the camshaft carrier 80, in the event that the camshafts 36, 37 are disposed upwardly apart from the mating surface 4 f, there can be avoided a problem that the machining properties of the cylinder head mating surface 4 f are reduced.

Namely, in the event that the camshafts are disposed upwardly apart from the mating surface, since the camshaft bearing portion protrudes upwardly of the mating surface 4 f, while the machining properties are reduced when compared with a case where the upper end surface of the cylinder head is flat, according to the embodiment, since the construction is adopted where the camshaft carrier 80 is detachably attached, the upper end surface of the cylinder head can be made flat and the machining properties can be improved.

Additionally, since the intermediate sprocket 38 a and the intermediate gear 38 b are rotationally supported by disposing the intermediate sprocket 38 a and the intermediate gear 38 b within the chain compartment 4 d and inserting the support shaft 39 so as to be disposed in such a manner as to extend across the chain compartment 4 d, the supporting construction can be simplified and the assembling properties can be improved.

Here, a backlash adjusting mechanism is provided between the intermediate gear 38 b and the camshaft gears 41, 42. This adjusting mechanism has a construction in which the intake camshaft gear 41 and the exhaust camshaft gear 42 are made up of two gears such as a driving gear (a power transmission gear) 46 and a shift gear (an adjusting gear) 45 and the angular positions of the driving gear 46 and the shift gear 45 can be adjusted.

Namely, the shift gear 45 and the driving gear 46 are fixed to flange portions 36 b, 37 b formed at end portions of the camshafts 36, 37, respectively, in such a manner that the angular positions thereof can be adjusted by four circumferentially long elongated holes 45 a, 46 a and four long bolts 68 a. A clearance portion 46 b is cut and formed in the driving gear 46 that is disposed outwardly, and only the shift gear 45 is fixed in such a manner that the angular position thereof can be adjusted two elongated holes 45 b and two short bolts 68 b by making use of the clearance portion 46.

A backlash adjustment is implemented according to the following procedure. Note that in the engine according to the embodiment, the intermediate gear 38 b rotates counterclockwise as shown in FIG. 3 when viewed from the left-hand side of the engine. Consequently, both the intake camshaft gear 41 and the exhaust camshaft gear 42 rotate clockwise. In addition, here, while the backlash adjustment will be described with respect to the intake camshaft gear 41, the same description would be made with respect to the exhaust camshaft gear 42.

Firstly, all the fixing bolts 68 a, 68 b of the intake camshaft gear 41 are loosened, and the shift gear 45 is rotated clockwise so that front side surfaces of teeth of the shift gear 45 in the clockwise direction slightly abut with rear side surfaces of teeth of the intermediate gear 38 b in the counterclockwise direction. In this state, the shift gear 45 is fixed to the flange portion 36 b of the camshaft 36 with two short bolts 68 b. Then, the driving gear 46 is rotated counterclockwise in such a manner that front side surfaces (driven surfaces) of teeth of the driving gear 46 in the counterclockwise direction abut with front side surfaces (driving surfaces) of the intermediate gear 38 b in the counterclockwise direction so as to obtain a required backlash, and in this state, four long bolts 68 a are tightened up, whereby the driving gear 46 and the shift gear 45 are fixed to the intake camshaft 36.

Thus, since the intake and exhaust camshaft gears 41, 42 are made up of the driving gear (power transmission gear) 46 and the shift (adjusting gear) 45 adapted to rotate relatively to the driving gear, respectively, the backlash can be adjusted by rotating the shift gear 45 relatively to the driving gear 46 forward or backward in the rotating directions.

Note that while, in this embodiment, both the driving gear 46 and the shift gear 45 which constitute the camshaft gears 41, 42 are described as being able to rotate relatively to the camshafts, one of the driving gear 46 and the shift gear 45 may be adapted to rotate relatively and the other gear may be integrated into the camshaft. In this case, it is desirable that the gear integrated into the camshaft constitutes the power transmission gear. Even if constructed in this way, similar function and advantage to those obtained by the embodiment can be obtained.

In addition, while, in the embodiment, the case has been described where the invention is applied to the valve train device which adopts the chain driving system, it goes without saying that the invention can also be applied to a valve train device which adopts a toothed belt driving system, and furthermore, the invention can also be applied to a valve train device in which the crankshaft and the intermediate gear are connected together via a gear train.

Next, a lubricating construction will be described. A lubrication system 50 of the engine according to the embodiment is constructed such that lubricating oil stored within a separate lubricating oil tank 51 is picked up and pressurized by a lubricating oil pump 52 via a down tube 56 c on a vehicle body frame, lubricating oil discharged from the pump 52 is divided into three systems such as a cam lubricating system 53, a transmission lubricating system 54 and a crank lubricating system 55 so as to be supplied to parts needing to be lubricated at the respective systems, and lubricating oil used for lubricating the respective parts needing lubrication is returned to the lubricating oil tank 51 by making use of pressure fluctuation occurring within the crank compartment 2 c as the piston 6 reciprocates vertically.

The lubricating oil tank 51 is formed integrally within a space surrounded by a head pipe 56 a, a main tube 56 b, the down tube 56 c and a reinforcement bracket 56 d of the vehicle body frame 56. This lubricating oil tank 51 communicates with a cross pipe 56 e which connects lower portions of the down tube 56 c via the down tube 56 c.

Then, the cross pipe 56 e communicates with a pick-up port of the lubricating oil pump 52 via an outlet tube 56 f connected thereto, an oil hose 57 a, a joint pipe 57 b and a pick-up passageway 58 a formed in a crankcase cover 10. A discharge port of the lubricating oil pump 52 is connected to an oil filter 59 via an oil discharge passageway 58 b, an external portion connecting chamber 58 c and an oil passageway 58 d and is divided into the three lubrication systems 53, 54, 55 on a secondary side of the oil filter 59.

The oil filter 59 is constructed such that an oil element 59 e is disposed in a filter compartment 59 d defined by detachably attaching a portion of a cover 47 to a filter recessed portion 10 b provided in the right case cover 10 by setting part thereof further back from the rest.

The cam lubricating system 53 has a construction which is generally constructed such that a lower end of a vertical member 53 a of a T-shaped lubricating oil pipe is connected to a cam side outlet 59 a of an oil passageway formed on the outside of the filter recessed portion 10 b, whereas left and right ends of a horizontal member 53 b of the lubricating oil pipe are connected to a camshaft oil supply passageway 53 c, so that lubricating oil is supplied to parts such as bearings of the camshafts 36, 37 which need to be lubricated via the passageway 53 c.

The transmission lubrication system 54 has the following construction. A right transmission oil supply passageway 54 a formed within the right case portion 2 b is connected to a transmission side outlet 59 b of the oil filter 59, and the oil supply passageway 54 a communicates with the interior of a main shaft bore 14 a formed in the main shaft 14 along the axial center thereof via a left transmission oil passageway 54 b formed in the left case portion 2 a. Then, this main shaft bore 14 a communicates with sliding portions between the main shaft 14 and change-speed gears via a plurality of branch bores 14 b, whereby lubricating oil supplied to the main shaft bore 14 a passes through the branch bores 14 b to be supplied to the sliding portions.

In addition, an intermediate portion of the left transmission oil passageway 54 b communicates with a bolt bore 60 a through which a case bolt 60 for connecting the left and right case portions 2 a, 2 b together is allowed to pass. This bolt bore 60 a is such as to be formed by forming a bore having an inside diameter which is slightly larger than the outside diameter of the case bolt 60 in tubular boss portions 60 c, 60 c which are formed so as to face and abut with each other on the mating surface between the left and right case portions 2 a, 2 b. The boss portion 60 c is situated in the vicinity of a portion where a gear train on the main shaft 14 meshes with a gear train on the drive shaft 15, and a plurality of branch bores 60 b are formed from which lubricating oil within the bolt bore 60 a is spouted out toward the gear trains meshing portion. Note that the bolts 60 shown in FIG. 19 as being developed into the left and right case portions are the same bolt.

Furthermore, a right end portion of the bolt bore 60 a communicates with a drive shaft bore 15 a formed in the drive shaft 15 along the axial center thereof via a communication bore 54 c. Then, the drive shaft bore 15 a is closed by a partition wall 15 c at a left-hand side portion and communicates with sliding portions between the drive shaft 15 and driving gears via a plurality of branch bores 15 b. Thus, lubricating oil supplied into the drive shaft bore 15 a passes through the branch bores 15 b to be supplied to the sliding portions.

The crank lubricating system 55 has the following construction. A crank oil supply passageway 55 a is formed in the filter cover 47 in such a manner as to extend from a crank side outlet 59 c toward the lubricating oil pump 52, and the passageway 55 is made to communicate with a communication bore 62 a which is formed in a rotating shaft 62 of the lubricating oil pump 52 to pass therethrough along the axial center thereof. Furthermore, the communication bore 62 a communicates with a crank oil supply bore 8 e formed in the crankshaft 8 to pass therethrough along the axial center thereof via a connecting pie 64. Then, this crank oil supply bore 8 e communicates with the interior of a pin bore 65 a in a crank pin 65 via a branch bore 8 f, and the pin bore 65 a is made to open to the rotating surface of a needle bearing 7 b at a big end portion 7 a of a connecting rod 7 via a branch bore 65 b. Thus, lubricating oil filtered in the oil filter 59 is supplied to the rotating surface of the needle bearing 7 b.

The lubricating oil pump 52 has the following construction. A pump compartment 61 c is provided in a right case 61 b of a two-piece casing made up of left and right cases 61 a, 61 b by setting a relevant portion of the case further back from the rest, and a rotor 63 is disposed rotationally within the pump compartment 61. The rotating shaft 62 is inserted into the rotor 63 along the axial center thereof in such a manner as to pass therethrough to be disposed in place therein, and the rotating shaft 62 and the rotor 63 are fixed together with a pin 63 a. Note that the oil pick-up passageway 58 a and oil discharge passageway 58 b are connected to a pump compartment upstream side and a pump compartment downstream side of the left case 61 a, respectively. In addition, reference numeral 66 denotes a relief valve for retaining the discharge pressure of the lubricating oil pump 52 to a predetermined value of lower and adapted to relieve the pressure on the discharge side of the lubricating oil pump 52 to the oil pick-up passageway 58 a side when the pressure on the discharge side reaches or exceeds the predetermined value.

The rotating shaft 62 is a tubular shaft which passes through the pump case 61 in the axial direction and opens to the crank oil supply passageway 55 a at a right end portion thereof as shown in the drawing. In addition, a power transmitting flange portion 62 b is formed integrally at a left end portion of the rotating shaft 62 as shown in the drawing. The flange portion 62 b faces a right end face of the crankshaft 8, and the flange portion 62 b and the crankshaft 8 are connected together by an Oldham's coupling 67 in such a manner as to absorb a slight deviation of the centers of the shafts.

The Oldham's coupling 67 is constructed such that a coupling plate 67 a is disposed between the crankshaft 8 and the flange portion 62 b, a pin 67 b planted in the end face of the crankshaft 8 and a pin 67 c planted in the flange portion 62 b are inserted into a connecting bore 67 d in the coupling plate 67 a.

In addition, the connecting pipe 64 is such as to connect a right end opening in the crankshaft 8 to a left end opening in the rotating shaft 62, and sealing is provided by an oil seal 64 a between the inner circumference of the crankshaft opening and the inner circumference of the rotating shaft opening and the outer circumference of the connecting pipe 64.

Here, as has been described above, the crank compartment 2 c is defined separately from the other transmission compartment 2 d, the flywheel magnet compartment 9 a and the clutch compartment 10 a, whereby an oil return mechanism is constructed in which the pressure within the crank compartment 2 c is fluctuated to be positive and negative as the piston 6 strokes, so that lubricating oil in the respective compartments is returned to the lubricating oil tank 51 by virtue of the pressure fluctuation.

To describe this in detail, a discharge port 2 g and a suction or pick-up port 2 h are formed in the crank compartment 2 c. A discharge port reed valve 69 adapted to open when the pressure within the crank compartment is positive is disposed in the discharge port 2 g, and a pick-up port reed valve 70 adapted to open when the pressure within the crank compartment is negative is disposed in the pick-up port 2 h.

Then, the discharge port 2 g communicates with the clutch compartment 10 a from the crank compartment 2 c via a communication bore 2 i and then communicates with the transmission compartment 2 d from the clutch compartment 10 a via a communication bore 2 j. Furthermore, the transmission compartment 2 d communicates with the flywheel magnet compartment 9 a via a communication bore 2 k. A return port 2 m formed so as to communicate with the flywheel magnet compartment 9 a communicates with the lubricating oil tank 51 via a return hose 57 c, an oil strainer 57 d and a return hose 57 e.

Here, a guide plate 2 n is provided at the return port 2 m. This guide plate 2 n has a function to ensure the discharge of lubricating oil by modifying the return port 2 m so as to provide a narrow gap a between a bottom plate 2 p and itself and to secure a wide width b.

Additionally, an oil separating mechanism for separating oil mists contained in the air within the tank by virtue of centrifugal force so as to return oil mists so separated to the crank compartment 2 c. This oil separating mechanism has a construction in which an introduction hose 72 a which is connected to an upper portion of the lubricating oil tank 51 at one end thereof is tangentially connected to an upper portion of a cone-shaped separating compartment 71 at the other end and a return hose 72 b connected to a bottom portion of the separating compartment 71 is connected to the pick-up port 2 h of the crank compartment 2 c. Note that the air from which the oil mists are separated is discharged to the atmosphere via an exhaust hole 72 c.

Thus, according to the embodiment, since the crank chamber 2 c is made to be a substantially closed space so that the pressure therein fluctuates as the piston 6 reciprocates vertically, whereby lubricating oil that has flowed into the crank compartment 2 c is sent back to the lubricating oil tank 51 by virtue of pressure fluctuation within the crank compartment 2 c, the necessity of an exclusive oil sending pump (a scavenging pump) can be obviated, and hence the construction of the engine can be simplified and costs can be attempted to be reduced.

In addition, since the discharge port reed valve (an outlet side check valve) 69 adapted to open when the pressure in the crank compartment increases and to close when the pressure lowers is disposed in the vicinity of where the oil sending passageway is connected to the crank compartment 2 c, the lubricating oil within the crank compartment 2 c can be sent back to the lubricating oil storage tank 51 in a more ensured fashion.

In addition, since an portion above the oil level within the lubricating oil storage tank 51 is connected to the crank compartment 2 via the return hoses 72 a, 72 b and the discharge port reed valve (a pick-up side check valve) 70 adapted to open when the pressure in the crank compartment 2 c lowers and to close when the pressure increases is provided in the vicinity where the return hoses are connected to the crank compartment 2 c, air required is picked up into the crank compartment 2 c when the piston 6 moves upwardly, whereas the inside pressure of the crank compartment 2 c increases as the piston 6 lowers, whereby lubricating oil within the crank compartment 2 c can be sent tout in a more ensured fashion.

Incidentally, in a case where there is provided no air supply path from the outside to the interior of the crank compartment 2 c, only a negative pressure or a lower positive pressure is formed inside the crank compartment, this causing a concern that there occurs a case where oil cannot be sent out properly.

Furthermore, since the centrifugal lubricating oil mist separating mechanism 71 for separating lubricating oil mist is interposed at the intermediate position along the length of the return passageways 72 a, 72 b, so that lubricating oil mist so separated is returned to the crank compartment 2 c via the return hose 72 b, whereas air from which the mist content is removed is discharged to the atmosphere, only lubricating oil mist can be returned to the crank compartment, whereby the reduction in oil sending efficiency can be avoided which would occur when an excessive amount of air is allowed to flow into the crank compartment, thereby making it possible to send out lubricating oil in the crank compartment in an ensured fashion while preventing the atmospheric pollution.

In addition, since the lubricating oil pump 52 is disposed so as to be connected to the one end of the crankshaft 8 and the discharge port of the lubricating oil pump 52 is made to communicate with the crank oil supply bore (an in-crankshaft oil supply passageway) 8 e formed within the crankshaft 8 via the communication bore (an in-pump oil supply passageway) 62 a formed within the lubricating oil pump 52 and the connecting pipe 64, the lubricating oil can be supplied to the parts of the crankshaft 8 which need to be lubricated by the simple and compact construction.

In addition, since the crankshaft 8 and the lubricating oil pump 52 are connected together by the Oldham's coupling 67 which can absorb the displacement of the shafts in the direction normal thereto and the communication bore 62 a and the crank oil supply bore 8 e are made to communicate with each other via the connecting pipe 64 with the O rings 64 a having elasticity being interposed between the connecting pipe 64 and the communicating bore 62 a, the crank oil supply bore 8 e, even in the event that the centers of the crankshaft 8 and the pump shaft 62 are caused to deviate slightly from each other, lubricating oil can be supplied to the parts needing to be lubricated without any problem, thereby making it possible to secure the required lubricating properties.

Furthermore, since the tubular boss portion 60 c is formed in the vicinity of the main shaft 14 and the drive shaft 15 which constitute the transmission, the crankcase connecting case bolt 60 is inserted into the bolt bore 60 a in the boss portion 60 c so that the space between the inner circumferential surface of the bolt bore 60 a and the outer circumferential surface of the case bolt 60 is made to form the lubricating oil passageway, and the branch bore (the lubricating oil supply bore) 60 b is formed which is directed to the change-speed gears at the boss portion 60 c, lubricating oil can be supplied to the meshing surfaces of the change-speed gears while obviating the necessity of providing an exclusive lubricating oil supply passageway.

In addition, since the other end of the lubricating oil passageway defined by the inner circumferential surface of the bolt bore 60 c and the outer circumferential surface of the case bolt 60 is made to communicate with an opening of the drive shaft bore (the lubricating oil passageway) 15 a formed within the drive shaft 15 which is situated opposite to an outlet side of the bore, lubricating oil can be supplied to the portions on the drive shaft 15 which are brought into sliding contact with the change-speed gears while obviating the necessity of providing an exclusive lubricating oil supply passageway.

Note that while the embodiment has been described as the invention being applied to a so-called DOHC engine which is provided with the intake camshaft and the exhaust camshaft, the invention can, of course, be applied to a so-called SOHC which is provided with a single camshaft which is made to function as both an intake camshaft and an exhaust camshaft as required.

INDUSTRIAL APPLICABILITY

According to the first and eighth aspects of the invention, since a reduction ratio from the crankshaft-side driving wheel to the intermediate driven wheel is set larger than a reduction ratio from the intermediate gear to the camshaft gear, the intermediate gear is made smaller in diameter than the intermediate driven wheel to such an extent that a pitch circle of the intermediate gear passes substantially an intermediate between a diameter of a boss and a pitch circle of the intermediate driven wheel and the intermediate gear is disposed behind the intermediate driven wheel and furthermore the inspection hole is formed in the intermediate driven wheel for visualizing the meshing portion where the intermediate gear and the camshaft gear mesh with each other, the meshing position between the intermediate gear and the camshaft gear can be visually observed easily and securely while the small-diameter intermediate gear is disposed behind the large-diameter intermediate driven wheel, thereby making it possible to carry out valve timing without any problem.

In addition, since the intermediate gear can be disposed behind the intermediate driven wheel, the dimension from the camshaft gear which meshes with the intermediate gear to the cam nose can be made shorter, and therefore, the torsional angle of the camshaft can be reduced accordingly, thereby making it possible to improve the valve opening and closing timing control accuracy. In addition, the area surrounding the camshaft can be made compact.

According to the second aspect of the invention, since the intermediate driven wheel and the intermediate gear are disposed on the crankshaft side across the mating surface of the cylinder head with the cylinder head cover, whereas the camshaft gear is disposed on the opposite side to the crankshaft side across the mating surface, the meshing portion where the intermediate gear meshes with the camshaft gear is positioned in the vicinity of the mating surface, there by making it possible to facilitate the visual observation of the meshing portion from the outside.

According to the third aspect of the invention, since the position alignment mark which refers to the mating surface as a reference surface is formed on the outer surface of the intermediate driven wheel, the alignment of the angular position of the intermediate driven wheel which is required in the first place in adjusting valve timing can be implemented easily and securely.

According to the fourth aspect of the invention, since the camshaft carrier is detachably attached to the cylinder head and the camshaft is rotationally mounted on the camshaft carrier by means of the camshaft cap, there can be eliminated a problem of the machining properties of the cylinder head mating surface being reduced which would result when the camshaft is disposed on the opposite side to the crankshaft side across the mating surface in such a manner as to be apart from the mating surface.

According to the fifth aspect of the invention, since the intermediate rotational unit into which the intermediate sprocket which is the intermediate driven wheel and the intermediate gear are integrated is disposed within the chain compartment formed on the side wall of the cylinder head and is rotationally supported by the support shaft which is inserted to be disposed across the chain compartment, the supporting construction of the intermediate rotational unit can be simplified and the assembling properties can be improved.

According to the sixth aspect of the invention, since the washer member is disposed between the intermediate rotational unit and the wall surface of the chain compartment for regulating the axial position of the intermediate rotational unit and the axial arrangement space for the bearing, commercially available bearings can be adopted without any machining, thereby making it possible to reduce costs.

According to the seventh aspect of the invention, since the camshaft gear is made up of the power transmission gear and the adjustment gear which is made to rotate relative to the power transmission gear, whereby the backlash is adjusted by causing the adjustment gear to relatively rotate forward in the rotating direction relative to the power transmission gear so that the tooth faces of the intermediate gear are held between the tooth faces of the adjustment gear and the tooth faces of the power transmission gear. 

1. An engine valve train device in which an intermediate driven wheel disposed in the vicinity of a camshaft is driven by a crankshaft-side driving wheel formed on a crankshaft and a camshaft gear fixed to the camshaft is driven by an intermediate gear disposed on a support shaft on which the intermediate driven wheel is disposed, the intermediate gear integrally rotating with the intermediate driven wheel, the engine valve train device being characterized in that a reduction ratio from the crankshaft-side driving wheel to the intermediate driven wheel is set larger than a reduction ratio from the intermediate gear to the camshaft gear, in that the intermediate gear is made smaller in diameter than the intermediate driven wheel to such an extent that a pitch circle of the intermediate gear passes substantially an intermediate between a diameter of a boss and a pitch circle of the intermediate driven wheel and the intermediate gear is disposed on a back side of the intermediate driven wheel, in that an inspection hole is formed in the intermediate driven wheel for visualizing a meshing portion where the intermediate gear and the camshaft gear mesh with each other, and in that an alignment mark is formed on a tooth portion of the intermediate gear and the camshaft gear, respectively.
 2. An engine valve train device as set forth in claim 1, characterized in that the intermediate driven wheel and the intermediate gear are disposed on a crankshaft side across a mating surface of a cylinder head with a cylinder head cover, whereas the camshaft gear is disposed on an opposite side to the crankshaft side across the mating surface, and in that the meshing portion where the intermediate gear meshes with the camshaft gear is positioned in the vicinity of the mating surface.
 3. An engine valve train device as set forth in claim 1 or 2, characterized in that a position alignment mark which refers to the mating surface as a reference surface is formed on an outer surface of the intermediate driven wheel.
 4. An engine valve train device as set forth in claim 2, characterized in that a camshaft carrier is detachably attached to the cylinder head, and in that the camshaft is rotationally mounted on the camshaft carrier by means of a camshaft cap.
 5. An engine valve train device as set forth in claim 4, characterized in that the intermediate driven wheel is an intermediate sprocket around which a timing chain is wound and is formed integrally with the intermediate gear to constitute an intermediate rotational unit, and in that the intermediate rotational unit is disposed within a chain compartment formed on a side wall of the cylinder head in such a manner that a rotational shaft of the intermediate rotational unit is located closer to the crankshaft side than the mating surface and is rotationally supported via a bearing by a support shaft which is inserted to be disposed in such a manner as to extend across the chain compartment.
 6. An engine valve train device as set forth in claim 5, characterized in that a washer member is disposed between the intermediate rotational unit and a wall surface of the chain compartment for regulating an axial position of the intermediate rotational unit and an axial arrangement space for the bearing.
 7. An engine valve train device as set forth in claim 6, characterized in that the camshaft gear comprises a power transmission gear for transmitting a driving force from the intermediate gear to the camshaft and an adjustment gear for adjusting a backlash between the power transmission gear and the intermediate gear, the adjustment gear being made to rotate relative to the power transmission gear, whereby the backlash is adjusted by causing the adjustment gear to relatively rotate forward in a rotating direction relative to the power transmission gear.
 8. An engine valve train device as set forth in claim 1, characterized in that an alignment mark is formed on each tooth portion of an intake camshaft gear and an exhaust camshaft gear disposed on the intake camshaft and the exhaust camshaft respectively and on a tooth portion of the intermediate gear, in that the intermediate driven wheel is formed with an inspection hole for visualizing the alignment marks of the intake camshaft gear and the intermediate gear and an inspection hole for visualizing alignment marks of the exhaust camshaft gear and the intermediate gear, and in that the alignment marks of the intake camshaft gear and the intermediate gear and the alignment marks of the exhaust camshaft gear and the intermediate gear are visible at the same time. 